Die-centering mechanism for type-casting and composing machines.



Patented Mav 2|. I90l.

.1. s. BANCROFT. I DIE BENTEBI NG MECHANISM FOR TYPE CASTING AND GOMPOSING MACHINES.

(Application filed Sept. 25, 1900.)

(No Model.)

2 Sheets -Sheat l.

wi/lmeooco No. 674,376. Patented May 2|, IBM.

,1. SIBANCROFT. DIE CENTERING MECHANISM FUR TYPE CASTING AND C'OMPOSING MACHINES.

(Application filed Sept. 26, 1900.) (No Model.) 2 Sheets-Sheet 2'.

UNITE STATES ATENT FFICE,

JOHN SELLERS BANOROFT, OF PHILADELPHIA, PENNSYLVANIA, ASSIGNOR TO THE LANSTON MONOTYPE MACHINE COMPANY, OF WASHINGTON,

DISTRICT OF COLUMBIA.

DlE-CENTERING MECHANISM FOR TYPE-CASTING AND COMPOSING MACHlll E S.

SPECIFICATION forming part of Letters Patent No. 674,376,- dated May 21, 1901.

Application filed September 25, 1900. Serial No. 31,014. No model.) i

To rtZZ whom it may concern:

Be it known that 1, Joint SELLERS BAN- CROFT, a citizen of the United States, resid ing at Philadelphia, in the county of Philadelphia and State of vPennsylvania, have invented certainnew and useful Improvements in Die-Centering Mechanisms for Type-Gasting and Composing Machines; and I hereby declare the following to be a full, clear, and exact description of the same, reference being had to the accompanying drawings, forming a part of this specification, and to the figu res of reference marked thereon.

This invention relates to improvements in or upon the die-centering mechanism of typecasting and composing machines of the kind illustrated in Patent No. 625,998, and has for its objects to increase the speed capacity of said mechanism and that of the machine as a whole as well as to diminish wear and breakage. One of the principal speed-limiting elements of said patented machine has been the die-centering mechanism or those portions of the machine which operate upon the die-case or its carrier to translate it from one position of adjustment to another. These motions are derived from the oppositely-movable jaws of the secondary positioning or gaging mechanism and are performed as said jaws close upon the secondary controller or shiftable gage, during which movement a part connected to the die-case or its carrier and lying between and in the plane of movement of the two jaws is engaged by one of the latter and brought into alinement with said shiftable gage, which determines the closed position of the jaws.

The centering of the die-case is but one of a sequence of operations to be performed in producing type, and it must be executed with promptness and certainty during a fraction of the rotation of the driving-shaft, each revolution of which measures the production and delivery of a single type. The force necessary to start the die-case is much greater than that required to maintain it in motion, and while these powers increase with the speed their ratios are different, being higher for starting than for continuing in mot-ion. Hence it was found in practice that when the speed of the driving-shaft exceeded a certain suddenly impelled or shot forward at a relatively high velocity and caused to impinge violently against the opposite or advancing jaw, thereby not only tending to check, displace, or break the latter or its connections, but reproducing the spring action. A sort of hammer action was thus developed which not only interfered with the proper positioningof the die within the limited time allowed for the purpose, but was very destructive in its action upon the mechanism, being so severe at times as to cause a rupture of the locking-teeth of the secondary controller. Two remedies were proposed the'introduction of an ordinary elastic coupling in the line of the driving mechanism and the application of brakes to the die-case and its carrier. The first of these tended rat-her to increase than to diminish the difficulty, the pressure stored in the spring reacting, as before, to drive the die-case across the interval between the oppositely-advancing jaws. Within certain limits the brakes were moderately efiective, but they absorbed power and produced excessive strains on the actuating devices, besides which the resistance interposed was constant, whereas the impelling force was variable. Hence there was a lack of accommodation. Now instead of favoring its development or attempting 'to apply a remedy after thedefect has been fully developed it is proposed to prevent develop ment of this destructive and interfering hammer action by removing the cause, and this has been accomplished by the interposition in the line of the driving mechanisin-as, for example, between the main actuating-lever and the prime mover or bell-crank of the positioning mechanism of an automatic compound frictional and elastic connection or coupling competent to limit and determine the degree of force and the time of its application both in starting the die-case and in continuing it in motion, said connection serving not alone to concentrate the spring action and measure the application of power both in time and extent, but also restricting the reactionary effect of compression by diminishing the effective quantity and prolonging the time of its application.

The coupling or connection referred to, of which a novel form and construction has been devised, is one comprising two movable members or sections, an interposed friction or clamping device operative to resist motion of the two members in either direction, and an elastic or yielding member operating to resist motion of the two first-mentioned members in one direction and to actuate the friction or clamping device in both directions. One of the two sections of the coupling is connected to the driving and the other to the driven element. When the pressure required for starting the die-case exceeds the maximum, as determined by the normal tension or resistance to motion of the elastic member, the latter yields (instead of the levers and other connections) and in so doing applies the brake, thereby prolonging and controlling the application of pressure until the inertia of the die-case has been overcome and it is started. Immediately this occurs the elastic member seeks to expand or resume its normal position and would do so at once, thereby impelling the die-case suddenly forward, were it not for the brake action, which operates at once to restrain the expansive force and by diminishing the latter prevents violent overthrow,with its consequent hammering,to such an extent that it becomes possible to both dispense with the brakes heretofore employed in connection with the die-case and its carrier and to increase the speed of the drivingshaft. The adjustment and action of this new connection renders desirable a slight change in the spring connections of the primary positioning mechanism, whereby said springs will be caused to operate in unison with instead of in opposition to the connection.

The invention also includes an improvement in the actuating mechanism for the locking-bolts, all as more fully described, and pointed out in the claims.

In the accompanying drawings, Figure 1 is a top plan view, and Fig. 2 is an end elevation,of the die-case-centering mechanism. Fig. 3 is a longitudinal sectional view of the automatic compound frictional and yielding connection. Fig. 4 is a detail showing one end of the casing. Fig. 5 is a detail view showing the sectional friction blocks, bolt, and collar in perspective. Fig. 6 is a view in perspective of the actuating devices for the locking-bolts. Fig. 7 is a top plan view of said locking mechanism.

Like numerals of reference in the several figures indicate the same parts.

The drawings illustrate the die or matrix centering mechanism of Patent No. 625,998, with the improvements applied thereto, and it will suffice for present purposes to identify the principal elements, it being understood that their functions and modes of operation are the same as those of the corresponding parts of the patent, to which latter reference may be had for a more detailed explanation.

The two sets of pins 1 constitute the primary controllers or gages for determining the closing points of the two sets of jaws 2, the latter forming the primary positioning or gaging mechanisms for locating the secoudary controllers or shiftable gages 3. The two pair of jaws 4-, constituting the secondary positioning or gaging mechanisms, cooperate with the secondary controllers or shiftable gages 3 to bring the die-case and its carrier to positions indicated by said controllers, each pair of jaws 4 in closing upon its controller 3 engaging a head 5, lying between said jaws and connected the one to the die-case and the other to the die case carrier.

The members of each set of jaws 2 are connected to a pair of levers 6, whose rear ends are connected by a link or coupling 7. One of the levers 6 is pivotally connected to the bed-plate and the other to one arm of the prime mover or bell-crank 8. Similarly the members of each pair of jaws 4 are connected to a pair of levers 9, whose opposite ends are united by a coupling 10, one lever of each pair being pivoted to the bed-plate and the other to the prime mover or bell-crank 8.

The retractor, comprising equalizing-bar l l and springs 12 and 13, has its spring 12 connected directly to the outer member of one pair of levers 6 between its pivot and jaw, as heretofore; but the other spring 13, instead of being connected mediately to the corre sponding member of the other set of levers 6 between its pivot and the point of attachment of link 7, is now connected to one arm of a bell-crank 14, whose opposite arm is connected bya link 15 to the lever 6 at a point intermediate its pivot and jaw. By this means a better balance is secured and a longer spring 13 may be employed, thereby rendering the action easier, the spring acting to assist the compound frictional and elastic connection instead of opposing it, as in the prior machine referred to.

16 represents the bolts for effecting the final adjustment and locking the secondary controllers or shiftable gages 3 after they have been brought to position by the jaws of the primary positioning or gaging mechanisms.

Heretofore the locking-bolts 16 were each furnished with a compression spring and driven positively in both directions through a single lever connected to the main actuating-lever for depressing the die-case, so that the labor of compressing the locking-bolt springs and the die-case-elevating springs was thrown at the same time upon said actuating-lever. To avoid this and secure a better balance in action, the spring reaction has been reversed and made to coincide with instead of oppose the main actuating-lever in seating the die. Accordingly each lockingbolt 16 is connected to one arm of a threearmed lever 20, there being preferably two such levers, both pivotally supported upon the same bolt. A tension-spring 21 is connected to the second arm of said lever, while the third arm projects in front of a block or head 22, carried by the actuating-rod 23. By means of this head 22 the locking-bolts are withdrawn against the tension of their springs and held from engagement with the secondary controllers 3 while the latter are being adjusted by the primary positioning mechanism; but when brought to position and while the die-case is being depressed head 22 is retracted, whereupon the springs advance and seat the locking-bolts.

With the exception of the actuating devices for the locking-bolts and the attachment of the spring-retractor, hereinbefore mentioned,

the foregoing description includes most, if not all, of the principal features of the die-centering mechanism of the prior patent, it being understood, of course, that the prime mover or bell-crank 8 was driven positively through a connection with the main actuating-lever.

Now the principal feature of the present invention has to do with the driving of the bellcrank 8 in such a manner that when the jaws 4 of the secondary positioning mechanism are brought together or caused to close on the secondary controller 3 the engagement of one of said jaws with the head 5 of the die-case or its carrier and the effort to start the latter will not develop the spring action throughout the system of actuating-levers and produce a hammering of the die-case on the jaws and the jaws on the secondary controller. With this end in view there is interposed between the main actuating-lever 25 and the rod or coupling 26, attached to the bell-crank 8, an automaticallyadjustable compound frictional and elastic connection, one type of which is represented in Fig. 3. In this the preferred form there is a hollow head or sleeve composed of two sections 27 28, adjustably connected, the innersection 28 beingprovided with a contracted portion or extension 29, furnishing both an internal shoulder and a means for detachably securing it to the threaded end of the actuating-rod 26. A keyhole-slot 30,Fig. 4, is provided in extension 29 for the ad mission and reception of the spherical head 31 on pin 32, the latter adj ustably secured in a socket in the main actuating-lever 25. The other section 27 of the casing is furnished with an internal tapered bearing 33 for the reception of the tapered clamp-sections 34, the latter surrounding and engaging the surface of a cylindrical bolt 35. This bolt 35 is furnished with to the end of rod 26, the proximate faces of said rod 26 and extension 37 being concaved to form bearings for the reception of spherical head 31. Riding loosely upon the bolt 35 and engaging the bases of the tapered clamp-sections 34 is a flanged collar 38, between which latter and the.flange 36 of bolt 35 is interposed a compression-spring 39. Spring 39 being normally under compression and interposed between the frictional clamping-sections 34 and the bolt 35 in the direction of the application of power in closing the jaws of the secondary positioning or gaging mechanism, it is caused to perform the double function of an elastic compressing device and a variable frictional resistant. Thus when in normal position, as shown in Fig. 3, the spherical head 31 of the main actuating-lever is embraced between the end of rod 26 and bolt 35, the spring holding the shoulder or flange 36 against its seat in the casing. At the same time the opposite end of the spring by hearing upon collar 38 forces the tapered clamping-sections 34 against the tapered bearing 33 and pressing them inward causes them to close in upon and clamp the bolt 35 with a force proportional to the pressure of the spring and the taper of the clamping-sections.

Preferably the tension or pressure of spring 39 is so adjusted that it will not yield under normal conditions-that is, when the power developed in starting the'die-case and its connections is slightly below the degree at which the driving connections will be placed under springtension. For example, let us suppose the adjustments and-proportions are such'that there will be no yielding of the bolt 35 within the casing until the pressure at the spherical head of the main actuating-lever equals or exceeds thirty pounds, below which amount the machine can safely be run without producing excessive overthrow or developing the destructive hammer action. If new conditions arise whereby the pressure reaches or exceeds the thirty pounds required to start bolt 35, spring 39 will yield slightly and in so doing will proportionally increase the friction upon bolt 35. Thus there will be produced a sufficiently gradual increase of pressure acting for a sufficient time to start the die-case and its connections, the excess of pressure being represented by the resistance of the spring plus the friction on bolt 35, as derived from the reaction of the spring upon the clamping-sections. Were it not for the frictional featurethat is, if the spring alone was employed to resist the movement of the bolt in the casing-the starting of the die-case would be accomplished; but instead of the spring of the driving connections there would be the reaction of the spring in the casing, which immediately the inertia of the die-case was' overcome would tend to advance the casing suddenly and withaforce equal to that stored in the spring by its compression, thus producing all the destructive effects of hammering, the spring in the connection merely replacing the spring of the driving connections and with the same disastrous results. Moreover, a simple compression-box, such as this would be without the friction-brake, would require considerable motion and a corresponding delay in the action of the jaws, besides being otherwise incompetent to deal with the problem because of its action in immediately giving out substantially the same amount of power expanded in compressing the spring.

The addition of the frictional feature cures the defect, for besides varying-that is, increasing-the frictional resistance to the movement of the bolt 35 in proportion to the amount of the excess of power applied in compressing the spring it both diminishes the amount of power and retards the reactionary eifect of compression. Thus in the example of the thirty-pounds excess pressure applied in effecting a compression of the spring a large percentage is absorbed in overcoming the friction on the bolt. So, too, when the inertia of the die-case is overcome and it starts on its journey the spring in expanding cannot deliver its full power in advancing the casing and with it the driving connections of the die-centering mechanism for the simple reason that in expanding it must still over come the frictional resistance established not only by the normal tension of the spring, but by the additional power resulting from further compression. The final result is that the excess of power amounting to, say, thirty pounds, which operated to advance the bolt 35 and compress the spring 39, is so largely absorbed in overcoming friction that but a fraction-say ten pounds-remains for effecting the advance of the casing and connected parts, the difference (twenty pounds) being absorbed or neutralized by the friction device, and even this small force is not expendedinstantly,butgradually,theamount and rate varying with the initial amount acting to eifect compression of the spring.

The foregoing is believed to be a substantially correct explanation of the action; but whether so or not the fact remains that by the use of this improved automatically-adjustable compound frictional and elastic connection the brakes heretofore used on the die-case and its carrier can be dispensed with without producing overthrow, and the machine can be run at a higher rate of speed without developing the objectionable hammer action referred to.

Having thus described my invention, what I claim as new, and desire to secure by Letters Patent, is-

2. In a centering mechanism such as described, the combination with its prime mover and the main actuating-lever, of a driving connection provided with a movable member, a friction device acting thereon, and a yielding tension device, such as a spring, arranged to oppose the movement of said movable member and actuate the friction device; substantially as described.

3. In a driving mechanism such as described, the combination with the driving and driven members arranged to permit independent movement, of a driving connection containing a friction-brake and a compressionspring, both acting together to resist the ap proach of the driving and driven members, the brake operating to retard the separation of the members under the influence of the spring after compression substantially as described.

4. In a centering mechanism such as described and in combination with its prime moverand the main actuating-lever, of ad riving connection comprising a sleeve or casing attached to the driven member and provided with an incline, a bolt engaging the driving member or actuating-lever and provided with a shoulder or flange, a brake device interposed between said bolt and incline, and a compression-spring interposed between the shoulder or flange of the bolt and the brake device, substantially as described.

5. An automatically-adjustable combined frictional and elastic driving connection for use in communicating motion from the main actuating-lever to a die-centering mechanism, the same including a casing provided at one end with means for attaching it to a driven rod and at the opposite end with an internal conical bearing-surface, conical clutch-sections engaging said conical bearing-surface, aboltextending between said clutch'sections, a compression-spring interposed between said clutch-sections and flange on the bolt, and a head carried by the main actuating-lever and taking its bearing between the bolt and the said driven rod, substantially as described.

6. A driving connection for die-centering mechanism such as described, including in its construction the sectional casing, flanged bolt, sectional clamp, loose collar, and com pression-spring combined and arranged substantially as and for the purpose set forth.

7. In a die-centering mechanism such as described, the combination with the lovers of the primary positioning or gaging mechanism of the retractor having its spring connected to the outer lever of each pair intermediate its pivot and jaw; substantially as described.

8. In a die-cen tering mechanism such as described, the combination with the levers of the primary positioning or gaging mechanisms, of a retractor having its spring connected to one lever of each pair at corresponding points intermediate its pivot and jaw, the

one immediately and the other mediately through a bell-crank lever and link; substantially as described.

9. In adie-centering mechanism such as described, the combination with the secondarycontroller-locking bolt, of a spring-actuated lever for advancing the bolt to locking position, and a power-actuated block engaging said lever to retract the bolt against the pressure of the spring, substantially as and for the purpose described.

described, the combination with the secondary controllers and their locking-bolts, of the three-armed levers, one for each bolt, one arm of each lever engaging a locking-bolt, another arm an actuating-spring, and the third arm of both levers engaged by a block on the actuating-rod; substantially as described.

JOHN SELLERS BANCROFT.

Witnesses:

FRANK G. GRIER JOSEPH B; CHURCH. 

